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    • 专利摘要:
    SUBMARINE HEAT EXCHANGER AND METHOD FOR TEMPERATURE CONTROL. The invention relates to an underwater heat exchanger for cooling or heating a hydrocarbon-containing fluid, said heat exchanger comprising: a section of convection surrounded by a shell or shell comprising: one or more heat exchanger inlets and outlets; one or more hydrocarbon-containing fluid inlets and outlets and one or more convection tubes that carry fluid adapted for heat transfer between the hydrocarbon-containing fluid inside the tubes on the opposite side of the tubes, where the heat exchanger is provided with one or more flow regulating devices to control the outlet temperature of hydrocarbon-containing fluid, in which the heat exchanger fluid circulates in a closed circuit for heat transfer with both said hydrocarbon-containing fluid and the surrounding seawater in the outside of the enclosure. The invention also relates to a method for cooling or heating a hydrocarbon-containing fluid.
    公开号:BR112013032865B1
    申请号:R112013032865-7
    申请日:2011-07-01
    公开日:2020-12-01
    发明作者:Baard Kaasa；Bernt Henning Rusten；Arne Olav Fredheim；Knut Arild Marak；Gunleiv Skofteland
    申请人:Equinor Energy As；
    IPC主号:
    专利说明:

    Field of invention
    [0001] The invention relates to a subsea heat exchanger unit with outlet temperature control and, in particular, a convection heat exchanger, for cooling or heating a fluid stream containing produced hydrocarbon, such as from of one or more subsea wells, and methods for such temperature control. Foundations
    [0002] The temperature of a hydrocarbon-containing stream produced at submarine level is generally hot and can normally vary at temperatures in the range of 30 to 150 ° C, at prevailing pressures. In order to process or transport a stream of hot hydrocarbon fluid it may be necessary to regulate the stream temperature, such as by cooling the stream to a specific temperature, for example, in the range 0 to 60 ° C.
    [0003] Several existing oil coolers located at the bottom of the sea are not controllable and have the limitation of only cooling the oil from a well stream after the phase gas separation. Such refrigerators are used to lower the oil temperature, either because of pipeline temperature restrictions or for other reasons.
    [0004] There are also several gas refrigerators installed underwater.
    [0005] A known type of subsea refrigerators consists of bundles of steel tubes, in which the hot process current flows. Sea water at about 4 ° C flows freely through the outside of the tubes, directly cooling the process stream by dissipating heat through the walls of the steel tube into the surrounding sea water. The amount of cooling depends heavily on the sea current, when the heat transfer is increased several times, if there is a strong sea current. In this way, the output temperature of the process current is given by uncontrollable variables. For some applications where any additional cooling is considered an advantage, this may be satisfactory.
    [0006] However, hydrocarbon fluids can develop depositions of wax and hydrate when cooled below certain temperatures. A formation of depositions of wax and / or hydrates inside tubes or process equipment will reduce the capacity of said parts and in the worst case, lead to blockage that prevents production and is both time consuming and expensive to remove. Therefore, the uncontrolled cooling of hydrocarbon fluids in subsea installations is undesirable, when the outlet temperature of such refrigerators can result in undesirable process conditions, such as temperatures below the hydrate or wax formation temperature in the fluid.
    [0007] In a subsea processing system more elaborate than oil cooling or gas compression, for example, for future controllable water knockout or hydrocarbon dew point control, the outlet temperature of a heat exchanger submarine must be controllable. This will allow the temperature of the outgoing process stream to be fixed, regardless of the change in flow streams, flow temperatures, sea temperature and marine currents.
    [0008] A temperature control of hydrocarbons containing process currents will also be advantageous for the control of hydrate as there is a risk in subsea systems of having areas cooled below the temperature of the hydrate (typically 20 to 30 ° C). To avoid deposits, such as hydrates, below said temperatures, hydrate inhibitors are added to the flow. Conventional hydrate inhibitors can be an alcohol (methanol or ethanol) or a glycol, such as monoethylene glycol (MEG or 1,2-ethanediol), which are inexpensive and simple to inject. However, the amount of hydrate inhibitor needed is proportional to the water content of the stream and at high levels it will require a hydrate inhibitor regeneration process at the receiving end.
    [0009] By controlling the flow of water through the bundle of tubes carrying a stream containing hydrocarbon, control of the refrigerator's outlet temperature can be provided. The current suggested way of carrying it out is to place the bundle of tubes in an enclosure (large tank, shell or coating) with openings at each end for the passage of seawater flow. The amount of sea water entering / leaving the tank, that is, the flow of sea water through the bundle of tubes, can be controlled in order to adjust the heat transfer coefficient and, consequently, the outlet temperature of the chain containing the hydrocarbon.
    [0010] WO 2008/147219, (FMC Kongsberg Subsea), concerns an underwater refrigeration unit having an inlet for a hot fluid and an outlet for a cooled fluid, the cooling unit that comprises a number of spirals exposed to sea water, and means for generating a flow of sea water in addition to spirals, in which the means for generating the flow of sea water comprise a propeller and a rotary actuator, and in which the refrigerator is included in a duct.
    [0011] WO 2010/002272, (Aker Subsea AS), concerns an underwater convection heat exchanger to cool or heat a fluid containing hydrocarbon in an underwater environment. The heat exchanger comprises a convection section with a fluid transport tube adapted for the transfer of heat between the hydrocarbon fluids carried out on one side of the tube wall and the surrounding water on the opposite side of the tube wall. The convection section is bounded by a housing with a seawater inlet and a seawater outlet and the heat exchanger is provided with means for controlled flow of seawater flow from the seawater inlet to the outlet of sea water.
    [0012] Consequently, the documents referred to above describe a control mechanism to regulate the flow of sea water through the bundle of tubes with a propellant or a pump, respectively.
    [0013] US 3158010 concerns a heat exchanger with helically wound tube bundles.
    [0014] The use of sea water for the direct cooling of tubes that carry the fluids containing relative hot hydrocarbon can give rise to unwanted flaking and marine development or bio fouling. Scaling can occur on surfaces with high temperatures in seawater, such as 60 ° C and above, by deposition of inorganic compounds, such as, for example, CaCO3 and CaSO4. Bio-fouling or development can occur in any subsea equipment, but it is intensified by hot temperatures, as in the hot tubes of a heat exchanger. In addition, high temperatures increase the risk of corrosion of the cooling pipes, which can lead to leakage and malfunction.
    [0015] The formation of flaking and scale on the pipe walls reduces the efficiency of heat transfer through the formation of an insulating film or a layer on the seawater side of the pipe surfaces and may, in addition, cause corrosion. The formation of such layers not only reduces the heat transfer and the efficiency of the heat exchanger, but can also decrease the passage path for the flow of sea water. These effects can either claim increased seawater yield, such as an increase in pump capacity or an over-dimensioning of the heat exchanger to compensate for the reduction in total heat transfer. Alternatively, regular cleaning of surfaces exposed to increased scale and scale may be necessary.
    [0016] The heat exchangers suggested in the prior art, with controllable outlet temperature, are subject to the scale and scale mentioned. Due to the tube bundle casings, in which seawater comes in contact with the hot hydrocarbon transport tubes, they are difficult or impossible to clean physically. In addition, the use of biocides and / or anti-flaking chemicals to remove such scale flakes is undesirable, due to the difficulty in dealing with such substances at an underwater level in a safe and controlled manner with regard to environmental aspects.
    [0017] Consequently, there is a need for an undersea heat exchanger with outlet temperature control, which is not subject to or less prone to the concerns of prior art heat exchangers. Summary and purpose of the invention
    [0018] The invention relates to an underwater heat exchanger and a method for controlling the temperature, by cooling or underwater heating a fluid containing hydrocarbon.
    [0019] The heat exchanger of the present invention is capable of cooling or heating any hydrocarbon-containing fluid, either a liquid or gas phase, possibly containing water, to varying degrees.
    [0020] Specifically, the heat exchanger can be designed for the cooling of a hydrocarbon-containing gas, which was previously separated from a multiphase flow by a separator, below a temperature as low as possible to knock out the water, but not for n the hydrate formation temperature region. Condensed water liquids and condensate can be separated from said gas by a second separator, such as a water condensate purifier providing a second gas phase, intensified for transport over long distances, possibly with the addition of a limited amount of hydrate inhibitor, the amount of which is significantly lower than the amount needed to transport the first phase of separate gas.
    [0021] In one aspect the invention relates to an underwater heat exchanger for cooling or heating a fluid containing hydrocarbon, said heat exchanger comprises; a convection section closed by a shell or casing comprising: one or more heat exchanger fluid inlets or outlets; one or more hydrocarbon-containing fluid inlets or outlets; and one or more convection tubes carrying fluid adapted for heat transfer between the hydrocarbon-containing fluid inside the tubes and a surrounding heat exchanger fluid on the opposite side of the tubes, where the heat exchanger is provided with one or more more flow regulation devices to control the outlet temperature of the hydrocarbon-containing fluid, in which the heat exchanger fluid circulates in a closed circuit, for heat transfer, both with said hydrocarbon-containing fluid and with the surrounding sea water outside the enclosure.
    [0022] The flow regulation device can be a pump or a compressor that regulates the flow rate of the heat exchanger fluid and, in addition, the convection tubes within the convection section are helically wound. In addition, the heat exchanger can be positioned vertically, optionally, to facilitate drainage.
    [0023] In addition, the closed circuit may comprise one or more external convection tubes adapted for the transfer of heat between the heat exchanger fluid inside the tubes and the surrounding sea water, on the opposite side of the tubes. In the case of two or more external convection tubes, which may be arranged in one of: a free parallel arrangement to be in a horizontal, vertical or inclined arrangement, a helical arrangement in a self-supporting manner or wrapped around the housing of the heat exchanger.
    [0024] In addition, the flow regulation device can be a propellant or ejector to increase the flow of surrounding sea water through the external convection tubes, optionally, in which the convection tubes are included within a cylindrical casing of open ends.
    [0025] The hydrocarbon-containing fluid and the heat exchanger fluid can flow in a co-current or counter-current manner and / or the flow of the heat exchanger fluid can be inverted.
    [0026] External convection tubes and / or internal convection tubes can be equipped with an electric heater to prevent flaking or development.
    [0027] The heat exchanger can comprise a distribution communication tube at the hydrocarbon-containing fluid inlet, optionally to distribute the fluid containing gas and liquid phase hydrocarbon in equal proportions across all internal convection tubes.
    [0028] The closed convection circuit can comprise a bypass circuit bypassing the external convection tubes and the flow regulation device can also be a valve in the diversion circuit regulating the rate of mixing of the heat exchanger fluid that passes through the external convection tubes and bypass.
    [0029] The fluid in the convection closed circuit can, in some cases, be mainly a gas device and, consequently, the flow can be a compressor, in which the closed circuit comprises an expansion valve, optionally at the inlet of the exchanger fluid heat from the convection section.
    [0030] In another aspect, the invention relates to a method for the underwater cooling or heating of a fluid containing hydrocarbon comprising: passing said hydrocarbon-containing fluid through one or more convection tubes in a closed convection section of a subsea heat exchanger; and passing said heat exchanger fluid around said convection tubes within said closed convection section, in order to cool or heat the hydrocarbon-containing fluid; and circulating said heat exchanger fluid in a closed circuit, through seawater outside the closed convection section, in order to cool or heat the heat exchanger fluid before entering the closed convection section of the heat exchanger again .
    [0031] The temperature of the hydrocarbon containing fluid that leaves the convection section of the heat exchanger can be regulated by the speed of the heat exchanger fluid flow, optionally by a pump or a compressor.
    [0032] The heat exchanger fluid can be passed through one or more convection tubes external to the closed circuit in seawater outside the closed convection section. In addition, the temperature of the hydrocarbon containing fluid leaving the convection section of the heat exchanger can be regulated by forcing a stream of sea water around said external convection pipes, optionally by a propellant or ejector.
    [0033] Some of the heat exchanger fluid that passes through the closed circuit, through sea water can be passed through a bypass line, bypassing one or more tubes of external convection and in which the mixing rate is regulated at least one valve on the bypass line and / or on the line comprising the external convection tubes. As a result, the temperature of the hydrocarbon-containing fluid that leaves the convection section of the heat exchanger can then be regulated by the speed of the mixture of heat exchange fluids that passes through the bypass line and / or the line comprising the convection tubes. external. Brief description of the drawings
    [0034] The invention will be described in further detail below, for example, by the embodiments with reference to the accompanying drawings, none of which should be construed as limiting the scope of the invention. It should be noted that the drawings are for illustrative purposes only. The dimensions of part and units represented in the drawings are not real and are only for illustration of the principles. Any combination of the elements shown in each separate embodiment is considered and can be applied in order to obtain the effect similar to the previous embodiment.
    [0035] Fig. 1 shows a side cross-sectional view of a first embodiment of a heat exchanger unit according to the invention.
    [0036] Fig. 2 shows a side view of the heat exchanger unit of figure 1.
    [0037] Fig. 3 shows a cross-sectional side view of a heat exchanger unit in a second embodiment of a heat exchanger unit according to the invention.
    [0038] Fig. 4 shows a side cross-sectional view of a heat exchanger unit of a third embodiment of a heat exchanger unit according to the invention.
    [0039] Fig. 5 shows a side cross-sectional view of a heat exchanger unit of an embodiment in front of a heat exchanger unit according to the invention.
    [0040] Fig. 6 shows a side cross-sectional view of a heat exchanger unit of a fifth embodiment of a heat exchanger unit according to the invention. Detailed description of the invention
    [0041] The term "process fluid" is intended to include any fluid that is cooled (or heated) by the heat exchanger in order to be processed or transported and possibly even further processed.
    [0042] The term "hydrocarbon-containing fluid" is intended to cover any type of liquid or gas or mixtures containing hydrocarbons, such as oil and / or gas from a production site, both without or with water in any amount.
    [0043] The term "heat exchanger" is used to understand any device or system in which a fluid is heated or cooled by convection with another fluid, due to temperature differences.
    [0044] Figure 1 shows a cross-sectional view of a first embodiment of the heat exchanger 1 according to the present invention. The heat exchanger 1 comprises a communication tube 10 and a convection section 20 in a shell or casing, said communication and convection tube section being sealed together by a partition 102. The volume of the communication tube 10 is bounded by an enclosure 101 and the partition 102 and receives process fluid through a process fluid inlet 11. The process fluid received by the communication tube 10 is distributed through the partition 102 to one or more internal convection tubes 13 that pass through the convection section 20, which is limited by a cylindrical casing or casing 201, a bottom wall 203 and said partition 102. The connector 10 can be a distribution communication tube which, in the case of a The process containing a mixture of oil and gas ensures an equal distribution of phases in each tube of internal convection, in order to avoid a local concentration of the phases in some tubes that can cause deposits.
    [0045] The internal convection tubes 13 are grouped together in a fluid outlet process 12 at the opposite end of the convection section.
    [0046] The layout of the internal convection tubes 13 inside the convection section 20 may vary, but are, in this example, helically mounted, as shown in figure 1, as in a helical spiral arrangement, in which a large heat transfer area can be activated within a small volume of the convection section.
    [0047] In a spiral heat exchanger, the total beam is formed as a cylindrical device with tubes wrapped in circular layers. All tubes are wound with a fixed angle of inclination. The end rolls of the tube are arranged in different layers, each level containing several tubes. The winding direction of each layer can be the same or alternating between layers. All tubes are the same length. The radial or longitudinal degree between the tubes can be flexibly varied.
    [0048] The convection section 20, being limited by the cylindrical casing 201, the bottom wall 203 and said partition 102, still comprise one or more heat exchanger fluid inlets 21 and one or more heat exchanger fluid outlets 22 , in which the heat exchanger fluid can pass freely over the included internal convection heat exchanger tubes 13. The heat exchanger fluid outlets 22 can be oriented in the longitudinal or radial direction and several outlets are preferable when directed in the radial direction, to avoid immobilized flow regions in parts of the convection section 20.
    [0049] As shown in figure 1, the heat exchanger exemplified in this embodiment is placed vertically and operated in a counter-current mode, in which the heat exchanger fluid 21 is placed near the seabed and the outlets heat exchanger fluid 22 are positioned at the top of the heat convection section part 20. The process fluid enters the upper side through the inlet 11 of the heat exchanger 1 and is drawn to the bottom of the convection section 20 through the outlet 12. The vertical positioning of the heat exchanger allows easy draining of liquids in the heat exchanger during stops.
    [0050] The convection section 20 of the heat exchanger 2 may preferably comprise a flow deflection element 202 or turbulence element, such as a housing, positioned within the center of the convection section 20, to direct the heat exchanger fluid more directly on the internal convection tubes and hinder the direct passage through the middle of the spiral arrangement of said tubes. The diverter element 202 can have any suitable shape and, in this embodiment, has a cylindrical shape centered in the middle of the convection section, with a shorter length than the section, positioned at a vertical distance between the inlet heat exchanger of fluid and connected to said division 102 at the top of the section. This arrangement directs the heat exchanger fluid to the most peripheral areas, at the bottom and upwards along the internal convection tubes 13 and, subsequently, outwards to the upper side outlets 22. The deflection element 202 can also provide structural resistance for the unit and can be used as a support for the internal convection tubes 13 inside the heat exchanger. Any suitable bypass elements and / or deflectors can be used to direct the flow of the heat exchanger fluid in an optimal way.
    [0051] Figure 2 shows an external side view of the heat exchanger 1 in figure 1. The heat exchanger fluid that leaves the convection section 20 through the upper outlets 22 is conducted in external convection tubes 23 arranged in a serpentine shape. outside the heat exchanger tank 1 in the cylindrical shell 201 towards the lower end, where they are collected in an inlet tube 24 before entering the heat exchanger again through the fluid inlet heat exchanger 21. O the number of external convection tubes 23 corresponds preferably to the number of outlets 21. The heat transfer between the housing 201 and the external convection tubes 23 is negligible. The heat transfer between housing 201 and the surrounding sea water can contribute to the total heat transfer.
    [0052] In the mode shown in the present embodiment, heat exchanger 1 is used to cool a process fluid by exchanging heat with a heat exchanger or fluid circulating in a closed or closed circuit of refrigeration. In this way, the natural convection inside the convection section 20, contributes to an increase in the buoyancy of the cooling fluid, which induces the upward flow of the cooling fluid. The coolant, being heated as the counter-current process fluid heats it, provides coolant circulation from the bottom to the top.
    [0053] With the use of a closed circuit for the heat exchanger fluid, any suitable fluid can be used, for example, sea water or glycol. In this way, the heat exchanger fluid can have inherent properties or be provided with properties, such as by means of additional substances, suitable to improve the heat exchange process, for example, to prevent scaling or internal development or to avoid or allow the phase change of the heat exchanger fluid.
    [0054] In the same way that the heat exchanger fluid is heated and advances in the convection section 20, into the tank 1, the external convection tubes 23 will heat the sea water that surrounds the heat exchanger of the tank 1 and seawater will advance due to increased buoyancy. This will intensify the circulation of sea water as the sea water will advance and will be replaced by cold sea water. The circulation of sea water can provide a certain countercurrent heat exchanger outside the tank 1, the cooling of the heat exchanger fluid before entering the convection section 20, of the heat exchanger 1 again. Normally, the sea current will provide an important flow of sea water through the external convection tubes 23 providing its convection.
    [0055] In order to control the outlet temperature of the process fluid, the circulation of the heat exchanger fluid is controlled. Temperature control can be achieved by controlling the flow rate of the heat exchanger fluid in order to regulate the heat transfer between the two fluids. Preferably, the circulation means in the form of a pump 50 is used to control the flow rate of the heat exchanger fluid. The alternative means of circulation means can be any of a propellant or ejector within the convection section 20 by forced circulation of the heat exchanger fluid between the internal convection tubes 13.
    [0056] Figure 3 shows another embodiment of the present invention in a cross-sectional view. The heat exchanger of the tank 2 comprises a convection section 40 limited by a cylindrical casing or casing 401, a bottom wall 403 and a top wall 404 and having a process fluid inlet 31 which distributes said process fluid in a or more internal convection tubes 33 that pass through the convection section 40 and being grouped into a process fluid outlet 32. The process fluid inlet 31 and outlet 32 can have any shape and connection position on the heat exchanger tank 2, for example, as shown in figure 1, but are, in this embodiment, positioned with the process fluid inlet 31 and an outlet 32 at the top and bottom, respectively, of the cylindrical housing 401. A The process fluid inlet can also comprise or be connected to a distribution communication tube, as shown in figure 1, for distributing the process fluid in the internal convection tubes 33.
    [0057] The arrangement of the internal convection tubes 33 within the convection section 40 can be helically mounted, as shown in figure 3, similar to the arrangement described above and shown in figure 1, or any other appropriate device.
    [0058] The convection section 40 further comprises a fluid inlet heat exchanger 41 and an outlet 42 in the lower and upper central part, respectively, of the convection section. The heat exchanger fluid can pass freely over the included internal helical heat exchanger convection tubes 33. In order to prevent said heat exchanger fluid from passing directly through the spiraling means of said internal convection tubes 33, a deflection member 402, cover or swirl member is placed in the center of the inner part of the convection section 40 to direct said fluid more directly over said tubes. The diverter element 402 can have any suitable shape and, in this embodiment, is in a cylindrical shape positioned in the middle of the convection section 40, with a shorter length than said section and positioned at a vertical distance between both the exchanger inlet fluid 41 as well as outlet 42. The diverter element guides the heat exchanger fluid out of the outermost areas of the convection section 40 at the bottom and upwards along the internal convection tubes 33, and in then back to the center again at the top of the convection section 40 towards exit 42.
    [0059] The heat exchanger 2 exemplified in figure 3, is also placed vertically and operated in a counter-current mode, as described above, in which the inlet heat exchanger fluid 41 is placed near the seabed and the outlet 42 is positioned at the top of the section 40 heat convection. The process fluid enters the top of the heat exchanger 2 via fluid inlet process 31 and is extracted at the bottom of the convection section 40 via the outlet process fluid 32. In this embodiment, both inlet 31 and outlet 32 are positioned in radial positions on the side of the heat exchanger 2.
    [0060] As shown in figure 3, the heat exchanger fluid leaving the convection section 40 of the upper outlet 42 is distributed to an external convection circuit 3. The convection circuit 3 comprises an arrangement for increasing the contact area with sea water, in the present example in the form of several external convection tubes 43 arranged in parallel, allowing sea water to surround said tubes and flow between them. The heat exchanger fluid is cooled as it flows through the convection circuit 3 and especially flows through said convection tubes 43, before being collected and taken to the heat exchanger 2 through the inlet 41. The heat exchanger fluid can be transported through the convection circuit 3 from the outlet 42 by a tube 44, by means of a pump 60 and a second tube 45 to the external convection tubes 43 through one or more divisions. Said external convection tubes 43 can be arranged in any suitable way, such as one or more of the parallel vertical tubes, horizontal or inclined parallel tubes or helical spiral arrangements, such as those described inside or outside the heat exchanger 1 , 2 and shown in more detail in figures 4 and 5. The separate convection tubes 43 are then joined and the heat exchange fluid is left by a tube 46 at the inlet 41.
    [0061] In the mode of this embodiment, the heat exchanger 2 is used for the cooling of a process fluid by heat transfer with a heat exchanger fluid by convection. This mode induces a natural convection within the convection section 40 which contributes to buoyancy within the section, as described above.
    [0062] The external convection tubes 43 will also heat the sea water around them and in the case of sea water they will still contribute to the circulation of sea water, once it is heated and replaced by cold sea water. However, the prevailing currents of seawater can often contribute to a more important flow of seawater through the external convection tubes 43 in a generally horizontal direction. Circulation can provide a certain countercurrent heat exchange outside the tubes 43, depending on the orientation of the tubes in relation to the existing or generated sea water flow, the cooling of the heat exchanger fluid before entering the convection section of the heat exchanger again. The flow of sea water around the disposed external convection tube 43 can also be improved and, in part, controlled by a flow device 70, such as a propellant, as shown in figure 3, by forced and controllable flow, in part of the sea water around the outer tubes 43, such as in an upward and / or crossed flow to obtain both natural and forced convection.
    [0063] In figure 3 a propellant, which forces the sea water through the external parallel tubes 43, exemplifies the flow device 70. In the same way, an ejector system for circulating sea water can be used, providing the water flow from the sea through the beam, sea water at high pressure being pumped through a single main tube, where the secondary sea water is ejected into the stream. The main seawater supply system, then, has high pressure and low volumetric flow, reducing the pump capacity (but increasing the pump head). The flow rate of sea water can be controlled to a certain extent and, in this way, controls the heat transfer, temperature profile and inlet temperature of the heat exchanger fluid to the convection section. A power supply pump system can be used for the injector system.
    [0064] In order to control the outlet temperature of the process fluid 32, the circulation of the heat exchanger fluid can be controlled. Temperature control can be achieved by controlling the flow rate of the heat exchanger fluid in order to regulate the heat transfer between the two fluids. The pump 60 can control the fluid rate of the heat exchanger fluid, ensuring the correct heat transfer rate between the heat exchanger fluid and the process fluid. The temperature of the heat exchanger fluid is still adjustable by the flow device 70, which can provide an increase in convection and thus an increase in the temperature difference of the heat exchanger fluid from the outlet to the inlet. Alternatively or in addition, the flow device 70 can contribute to keeping the inlet temperature of the heat exchanger fluid at the inlet 41 constant with the increase or decrease in the flow of sea water along the tubes 43 in adjusting the changes in the temperature of the sea and, especially, changes in currents.
    [0065] The external convection circuit 3 can also comprise a hydrostatic equalizer 61 to pressurize the inside of the tubular members of the convection circuit, so that the internal pressure is balanced with the sea water outside. In addition, the convection circuit 3 can optionally comprise a buffer tank for heat exchanger fluid (not shown). Differences in pressure inside subsea tubes and pipes or any equipment that requires thick-walled elements to withstand the hydrostatic pressure of seawater at real marine depth. By the pressure balancing the tubes and pipes and other elements of the external convection circuit, and especially the external convection tubes, the thickness of said tubes can be reduced and more effective cooling is obtained with sea water. In addition, such a pressure balance allows the use of other materials for steel tubes, such as, for example, aluminum.
    [0066] In order to further control the cooling of the heat exchanger fluid, a bypass line 47 in the convection circuit 3 with the external convection tubes 43 may be present, with a flow control valve 48 that regulates the quantity of fluid bypassing the external convection tubes 43. The amount of heat exchanger fluid that passes through the bypass line 47 will influence the final temperature of the heat exchanger fluid entering the convection section 40 at the inlet 41 as the fluids from the bypass 47 and the fluid still being cooled in the external convection tubes 43 are mixed at rates, depending on the control valve 48. As a result, the circulation pump 60 can rotate at a constant speed, while valve 48 controls the resulting temperature at inlet 41. With a seawater temperature in the range of 0 to 4 ° C, the inlet temperature of the heat exchanger fluid, for example, can be adjusted to be within an inter temperature range of about 15 to 25 ° C. Deviation 47 is also advantageous in the event of any leakage in the system, such as in external convection tubes 43.
    [0067] Figure 4 shows a heat exchanger similar to figure 3, in which the external convection tubes 53 of the convection circuit 3 are arranged in the form of a helical spiral of a vertical tube, in a vertical position. In this configuration, sea water can be heated and contribute to circulation along the tubes and through the tube that forms the tube layout, due to increased buoyancy when sea water is heated and replaced with cold sea water.
    [0068] An optional bypass line 47 of the external convection tubes 53 with a flow control valve 48 that regulates the amount of fluid bypassing the external convection tubes 53 is also shown. Valve 48 provides the possibility to take into account differences in temperature and seawater currents that affect the final temperature of the fluid leaving the external convection tubes 53, when it is not present in the flow device to adjust the water flow around the external convection tubes 53.
    [0069] Figure 5 shows another embodiment of a heat exchanger similar to that of figures 3 and 4, in which the external convection tubes 54 of the convection circuit 3 are also arranged in the form of a helical spiral of a tube, but where the tube is positioned horizontally.
    [0070] In order to obtain greater control of the cooling or heating effect of the external convection tubes 54, the tubes are, in this embodiment, partially surrounded by an optional cylindrical shell 71 with open ends, in which the water flow of the sea along external convection tubes 54 is controlled by a flow device 70. A propellant here exemplifies the flow device 70, but an ejector or similar device can also be used for the forced flow of sea water along and around said convection tubes 54 by forced convection. In another embodiment, housing 71 may also comprise deflectors or devices for closing and opening one or both openings at the ends of the housing (not shown), such as for additional control through the flow or to close housing 71, such as as for cleaning purposes.
    [0071] As mentioned above, the heat exchanger of the present invention can also be used for the heating of process fluids, by exchanging heat with sea water hotter than the process fluid.
    [0072] Figure 6 shows another embodiment of a heat exchanger according to the present invention, in which a heat exchanger 102 with the convection circuit 103 can be used as a vapor compression cooling system. The heat exchanger 103 is similar to the heat exchangers of the old embodiments of figures 3, 4 and 5, except for a heat exchanger fluid inlet 141 positioned on the side wall of its housing 201, at a vertical distance between the part bottom of said heat exchanger 102, instead of at the bottom. The convection circuit 103 is also similar to the embodiment of figures 3, 4 and 5, but it consists of a compressor 160, instead of a pump and, in addition, an expansion valve 164 in the convection exchange circuit heat before fluid 141 enters the heat exchanger. Thus, in the present embodiment, the heat exchanger circuit and convection is adapted to use a refrigerant that circulates as a heat exchanger fluid, for example, propane.
    [0073] The heat exchanger 102 works as an evaporator. By exchanging heat with the refrigerant, which is evaporated, the process fluid that passes through the internal convection tubes 233 is cooled. The refrigerant vapor in the gas phase exits the convection section 240 of the heat exchanger 102 through the fluid outlet of the heat exchanger 142 and fed through a tube 144 to the compressor 160 where the steam is compressed. The compressed steam gas is transported to an arrangement of external convection tubes 153 of a tube 145. In this embodiment, the external convection tubes 153 of the convection circuit 103 are arranged in the form of a helical spiral of a vertical tube, in vertical position, as in figure 4. The arrangement of the convection tubes can, however, take any shape that is suitable, for example, any of the above mentioned adjustments or any other suitable arrangements.
    [0074] The external convection tubes 153 function as a condenser where the compressed refrigerant vapor is condensed, comprising mainly a liquid by exchanging heat with cold sea water.
    [0075] The liquid refrigerant from the convection tubes 153 is transported by a tube 146 to the said expansion valve 164 from which the refrigerant outlets as a mixture of fluids in two phases and enters the convection section 240 of the heat exchanger 102 through inlet 141. Said inlet can be positioned above the level of the refrigerant liquid in the heat exchanger, as shown in figure 6, leaving the tube heat exchanger 233 partially immersed in the liquid phase of the refrigerant 203 and the space for the refrigerant vapor 204 from a top part of the convection section 240.
    [0076] The process described above will work even with a variable effect on the external convection tubes 153 for seawater as the variation in refrigeration will give rise to a variation in the gas and liquid ratio from the expansion valve. The temperature of the inlet flow in the convection zone 240 per inlet 141 will be constant and the cooling of the hydrocarbon fluid can be controlled by regulating the circulation speed of the compressor 160 to account for variations in the cooling of the marine currents.
    [0077] The convection system described above can, for example, be used as a second phase of hydrocarbon fluid refrigeration that, essentially, most of the water has been eliminated by a previous cooling and separation phase. The mechanism and the process can, for example, be used to reduce the dew point of a hydrocarbon gas below the temperature of sea water, such as for the production of dry gas.
    [0078] Example
    [0079] A cooling system according to the embodiments of figures 3 to 5 can receive a hot gaseous hydrocarbon produced from an underwater well at about 100 bar and 80 ° C in the quantities of about 60 kg / s. An inlet passes the said gas to the internal convection section of the heat exchanger and passes the gas inside the convection tubes thereof, when the gas can be cooled to an outlet temperature of about 25 ° C. The fluid heat exchanger, in this case the water in the amount of about 55 kg / s enters the heat exchanger at about 15 ° C and 30 bar and passes over the outer surface of said convection tubes inside the heat exchanger enclosure through of the internal convection section and is heated to an outlet temperature of about 60 ° C. The heat exchanger fluid is then directed through the external convection circuit, where it is cooled to about 15 ° C before entering the internal convection section. The amount of sea water at about 4 ° C and 30 bar necessary to obtain the cooling of the heat exchanger fluid mentioned is in the order of 3,500 kg / s, which passes over the external circuit, and especially the convection tubes. , by natural current or by forced flow using a flow device, as mentioned in the above embodiment.
    [0080] In comparison with the submarine heat exchangers of the prior art, in which sea water is used in direct contact with the convection tubes that carry the process fluids, the present invention makes use of a closed circuit, containing a heat exchanger fluid for heat transfer, with said convection tubes and, in turn, which exchange heat with sea water for external convection tubes. Thus, the surface temperature of the external convection circuit, ie tubes 23, 43, 53, 54 and 154 is reduced compared to the surface temperature of the inner tubes 13 and 33 and can be kept below the temperature at which it occurs flaking and at a temperature where marine development and corrosion are reduced. In addition, the external positioning of the external convection circuit may allow physical scraping and removal of marine scale and improved scale control.
    [0081] Therefore, the present invention also increases the fouling control and, consequently, limits the need for overcapacity in construction of subsea heat exchanger and provides a more precise temperature control.
    [0082] Most subsea coolers of the prior art are passive or have only limited means of controlling the direct flow of sea water through the heat exchanger tubes containing hydrocarbon fluid. The lack of accuracy in controlling the temperature of these previous coolers, therefore, the temperature level in said coolers can safely cool a hydrocarbon fluid without risking hydrate or other deposits.
    [0083] The invention provides the possibility to control the temperature of the fluid on the side of the tube (like hot fluid) at all down rates and can use both forced and free convection on the seawater side. The temperature of the process flow is controllable and the risk of hydrate formation is considerably reduced.
    [0084] The closed circuit allows for more complex tube arrangements, as well as bypass elements and deflectors within the convection section of the heat exchanger, as the fouling and growth of marine organisms are eliminated. The heat exchanger fluid may be water or any mixture of water or glycol or any mixture thereof, and may contain scaling and growth inhibitors, such as biocides or cleaning chemicals that keep the closed circuit free of contaminants and deposits.
    [0085] It should be noted that the process fluid which, in general, will be a hydrocarbon-containing fluid is preferably operated through the convection tube side of the internal convection tubes 13 and 33, in order to obtain a homogeneous cooling of the fluid, although the opposite is possible by the operation of the closed circuit connected to the heat exchanger fluid for the internal convection tubes 13 or 33 for the exchange of moderate heat. The criteria for this opposite operating mode must be that hydrocarbon-containing fluids are not cooled below any wax and / or hydrate formation temperature and therefore do not allow any precise control when the temperature inside the convection section varies with respect to the distance and contact with the internal convection tubes.
    权利要求:
    Claims (22)
    [0001]
    1. Underwater heat exchanger for cooling or heating a hydrocarbon-containing fluid, said heat exchanger comprising; • a convection section closed by a shell or enclosure comprising: one or more heat exchanger fluid inlets and outlets; one or more hydrocarbon-containing fluid inlets and outlets; and one or more convection tubes carrying fluid adapted for heat transfer, between the hydrocarbon-containing fluid inside the tubes and a surrounding heat exchanger fluid on the opposite side of the tubes, where the heat exchanger is provided with a or more flow regulation devices to control the outlet temperature of the hydrocarbon-containing fluid, characterized by the fact that the heat exchanger fluid circulates in a closed circuit, for heat transfer, both with said hydrocarbon-containing fluid and with the surrounding sea water outside the enclosure.
    [0002]
    2. Heat exchanger according to claim 1, characterized by the fact that the flow regulation device is a pump or a compressor that regulates the flow rate of the heat exchanger fluid.
    [0003]
    Heat exchanger according to claim 1 or 2, characterized in that the convection tubes within the convection section are helically spiraled.
    [0004]
    Heat exchanger according to any one of claims 1 to 3, characterized in that the heat exchanger is positioned vertically, optionally to facilitate drainage.
    [0005]
    Heat exchanger according to any one of claims 1 to 4, characterized in that the closed circuit comprises one or more external convection tubes adapted for the heat transfer between the heat exchange fluid inside the tubes and water of the sea surrounding the opposite side of the tubes.
    [0006]
    Heat exchanger according to any one of claims 1 to 5, characterized by the fact that two or more external convection tubes are arranged in one of: a free-standing parallel arrangement in a horizontal, vertical or inclined arrangement; a helical arrangement in a free standing manner or wrapped around the heat exchanger housing.
    [0007]
    Heat exchanger according to any one of claims 1 to 6, characterized in that the flow regulation device is a propellant or ejector to increase the flow of surrounding sea water through the external convection tubes, optionally in that the convection tubes are grouped within an open-ended cylindrical shell.
    [0008]
    Heat exchanger according to any one of claims 1 to 7, characterized in that the hydrocarbon-containing fluid and the heat exchange fluid flow in a co-current or counter-current manner.
    [0009]
    Heat exchanger according to any one of claims 1 to 8, characterized in that the flow of heat exchange fluid can be reversed.
    [0010]
    Heat exchanger according to any one of claims 1 to 9, characterized in that the external convection tubes and / or the internal convection tubes are equipped with an electric heater.
    [0011]
    Heat exchanger according to any one of claims 1 to 10, characterized in that the heat exchanger comprises a distribution communication tube at the hydrocarbon-containing fluid inlet, optionally for distributing fluid containing gas-phase hydrocarbon and liquid in equal ratios in all internal convection tubes.
    [0012]
    Heat exchanger according to any one of claims 1 to 11, characterized in that the closed convection circuit comprises a bypass circuit that bypasses the external convection tubes.
    [0013]
    13. Heat exchanger according to any one of claims 1 to 12, characterized in that the flow regulation device is a valve in the bypass circuit that regulates the mixing rate of the heat exchanger fluid that passes through the heating tubes. external convection and bypass.
    [0014]
    Heat exchanger according to any one of claims 1 to 13, characterized in that the hydrocarbon-containing fluid is mainly a gas.
    [0015]
    Heat exchanger according to any one of claims 1 to 14, characterized in that the flow regulating device is a compressor and the closed circuit comprises an expansion valve, optionally to the heat exchanger fluid inlet of the section convection.
    [0016]
    16. A method for underwater cooling or heating of a hydrocarbon-containing fluid comprising: • passing said hydrocarbon-containing fluid through one or more convection tubes in a closed convection section of an underwater heat exchanger; and • passing said heat exchanger fluid around said convection tubes within said closed convection section, in order to cool or heat the hydrocarbon-containing fluid; characterized by the fact that the method comprises the circulation of said heat exchanger fluid in a closed circuit, through sea water outside the closed convection section, in order to cool or heat the heat exchanger fluid before entering the section closed convection of the heat exchanger again, in which the temperature of the hydrocarbon-containing fluid leaving the convection section of the heat exchanger is regulated by one or more flow regulation devices.
    [0017]
    17. Method according to claim 16, characterized in that the one or more flow regulation devices comprises a pump or a compressor.
    [0018]
    18. Method according to claim 16 or 17, characterized in that the heat exchange fluid is passed through one or more external convection tubes of the closed circuit in seawater outside the included convection section.
    [0019]
    19. Method according to claim 18, characterized in that the temperature of the hydrocarbon-containing fluid leaving the convection section of the heat exchanger is regulated by forcing a stream of seawater around said external convection tubes , optionally by a thruster or ejector.
    [0020]
    20. Method according to any of claims 16 to 19, characterized in that some heat exchange fluid that passes through the closed circuit through seawater is passed through a bypass line, which deflects the one or more external convection tubes and where the mixing rate is regulated by at least one valve on the bypass line and / or the line comprising the external convection tubes.
    [0021]
    21. Method according to claim 20, characterized by the fact that the temperature of the hydrocarbon-containing fluid leaving the convection section of the heat exchanger is regulated by the mixing rate of the heat exchange fluids that pass through the bypass line and / or the line comprising the external convection tubes.
    [0022]
    22. Use of a heat exchanger, characterized by the fact that it is as defined in any one of claims 1 to 15, characterized by the fact that it is for cooling or heating a fluid containing hydrocarbon in an underwater environment.
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    同族专利:
    公开号 | 公开日
    GB2506798A|2014-04-09|
    GB201400889D0|2014-03-05|
    WO2013004277A1|2013-01-10|
    NO20140108A1|2014-01-30|
    AU2011372734B2|2017-01-05|
    AU2011372734A1|2014-02-20|
    NO342365B1|2018-05-14|
    US10317109B2|2019-06-11|
    CA2840701A1|2013-01-10|
    GB2506798B|2018-04-25|
    US20140246166A1|2014-09-04|
    BR112013032865A2|2017-07-04|
    CA2840701C|2019-07-30|
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    法律状态:
    2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-09-17| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-09-01| B09A| Decision: intention to grant|
    2020-09-29| B25D| Requested change of name of applicant approved|Owner name: EQUINOR ENERGY AS (NO) |
    2020-12-01| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 01/07/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    PCT/EP2011/061149|WO2013004277A1|2011-07-01|2011-07-01|Subsea heat exchanger and method for temperature control|
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